US20020141860A1 - Turbine pump - Google Patents
Turbine pump Download PDFInfo
- Publication number
- US20020141860A1 US20020141860A1 US10/107,209 US10720902A US2002141860A1 US 20020141860 A1 US20020141860 A1 US 20020141860A1 US 10720902 A US10720902 A US 10720902A US 2002141860 A1 US2002141860 A1 US 2002141860A1
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- United States
- Prior art keywords
- pump
- impeller
- blades
- fuel
- outer ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
- F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
- F01D1/12—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines with repeated action on same blade ring
Definitions
- the present invention relates to a turbine pump that is suitable to a fuel pump to be mounted in a fuel tank of an automotive vehicle.
- U.S. Pat. No. 5,468,119 or its corresponding publication JP-A-299983 discloses a turbine pump or peripheral pump for a fuel pump to be mounted in an automotive vehicle.
- the disclosed turbine pump has an outer ring at the circumference of an impeller, which is disposed in chamber walls or a pump casing.
- the outer ring is disposed outside the spaces (hereinafter referred to the impeller grooves) between blades of the impeller in the radial direction.
- the outer ring which is disposed around the impeller grooves, has axial end surfaces flush with the axial end surfaces of the blades.
- the outside diameter of the impeller is larger than the outside diameter of a pump passage that is formed in the casing and the outer ring is located close to the axial end surface of the pump casing.
- the axial distance between the impeller and the casing is arranged to be between several micrometers ( ⁇ m) and tens of micrometers to prevent high-pressure fuel from leaking from the outlet side of the pump to the inlet side thereof.
- the circumferential speed is so high that the outer ring is subject to wear, which lowers pumping capacity and the lifetime thereof.
- an impeller of a turbine pump has a plurality of blades disposed in the circumferential direction thereof, a plurality of impeller partitions respectively disposed between every two of the blades thereby forming a plurality of impeller grooves at front and rear sides of the partitions and an outer ring disposed at the peripheral edge of the blades.
- Each impeller groove, each pump passage and the outer ring form a circular space for circulating fuel thereby pressuring and discharging the fuel.
- the outside diameter of the impeller is smaller than the outside diameter of the pump passages. Therefore, the peripheral portion of the impeller is disposed within the pump passages where the impeller does not contact any surface of the pump passages. It is more preferable that the axial ends of the outer ring are positioned within axial ends of the blades.
- the outer ring may have axial ends that are tapered off in the radially inward direction.
- FIG. 1 is a partially cross-sectional side view of a turbine pump according to a first embodiment of the invention
- FIG. 2 is a fragmentary enlarged cross-sectional side view of a portion of the turbine pump shown in FIG. 1 encircled by circle II;
- FIG. 3 is cross sectional view of a portion of the turbine pump shown in FIG. 1 cut along line III-III;
- FIG. 4 is a fragmentary enlarged perspective view of a portion of the turbine pump shown in FIG. 3 encircled by circle IV;
- FIG. 5 is a fragmentary cross-sectional view of an impeller of a turbine pump according to a second embodiment of the invention.
- FIG. 6 is a fragmentary cross-sectional view of an impeller of a turbine pump according to a third embodiment of the invention.
- FIG. 7 is a fragmentary cross-sectional view of an impeller of a turbine pump according to a fourth embodiment of the invention.
- a turbine pump according to a first embodiment of the invention to be mounted in a fuel tank for an engine (not shown) is described with reference to FIGS. 1 - 4 .
- a turbine pump 1 is mounted in a fuel pump 100 together with a drive motor (not shown), which are covered by a housing 101 .
- the fuel pump includes, besides the drivemotor, a motor shaft 102 , an electric connector 103 , a fuel chamber 104 , a fuel discharge pipe 105 and a fuel intake pipe 4 a .
- the turbine pump 1 pumps up fuel in a fuel tank from an intake pipe 4 a and discharges the fuel from the turbine pump into the fuel chamber 104 . Thereafter, the fuel is supplied to an engine via the fuel discharge pipe 105 .
- the fuel chamber 104 is provided inside the drive motor.
- the turbine pump 1 is comprised of a pump casing 2 , an impeller 3 , and a pump cover 4 .
- the impeller 3 is rotatably disposed between the pump casing 2 and the pump cover 4 .
- the pump casing 2 is made of aluminum die-cast or strong resinous material that is resistant to fuel and has a cylindrical space 2 a that accommodates the impeller 3 .
- the axial depth of cylindrical space 2 a is a distance between several micrometers ( ⁇ m) and tens of micrometers longer than the thickness of the impeller 3 .
- the gap between the pump cover 4 and the impeller is the same as the gap between the pump casing 2 and the impeller 3 .
- a pump passage 2 b is formed to be coaxial with the cylindrical space 2 a .
- the pump passage 2 b is connected to the inlet 4 c at an end thereof and connected to the outlet 2 c at the other end thereof.
- the inlet 4 c is indicated in FIG. 3 by one-dot-chain line for reference.
- radially outermost surface 2 bl of the pump passage 2 bl is included in the inner surface 2 al of the cylindrical space 2 a .
- the outside diameter of the pump passage 2 b is the same as the inside diameter D 2 of the cylindrical space 2 a .
- a plurality of blades 3 a is formed at the axial end surface 3 g of the impeller 3 .
- the radial distance between the outside diameter D 1 of the impeller 3 and the inside diameter D 2 of the cylindrical space 2 a is designed to be the best for pump performance.
- the outside diameter D 1 of the impeller 3 is designed to be smaller than the outside diameter of the pump passage 2 b . Accordingly, the portion of the impeller 3 whose circumferential speed is the maximum while the impeller rotates does not contact the surface of the pump passage 2 b or any other portion of the pump casing 2 .
- the pump casing 2 has a bearing 5 that rotatably supports a motor shaft 102 at the center thereof.
- the impeller 3 is made of heat resistant resinous material and is disposed in the cylindrical space 2 a of the pump casing 2 . As shown in FIG. 3, the impeller 3 has a plurality of blades 3 a formed at both the peripheral front surface that faces the pump casing 2 and the peripheral rear surface that faces the pump cover 4 . The blades 3 a formed at the front surface and the blades formed at the rear surface are disposed side by side at equal intervals in the circumferential direction. An impeller groove 3 b is formed between each adjacent two blades 3 a . As shown in FIG.
- impeller partitions 3 d are disposed at an axially middle and radially inside portion thereof to protrude radially outward to divide each of the impeller grooves 3 b into a front side groove and a rear side groove.
- the fuel introduced in the space (hereinafter referred to as the circular space) defined by the impeller grooves 3 b , the pump passage 2 b of the pump casing 2 and a pump passage 4 b of the pump cover 4 is circulated and pressured by the impeller 3 .
- An outer ring 3 c is integrated with the plurality of blades 3 a to connect the same at the edges thereof. In other words, the outer ring 3 c closes the circumference of the impeller 3 .
- the axial ends of the outer ring 3 c are positioned within the axial ends of the impeller 3 .
- the outer ring 3 c has a trapezoidal cross section with the shorter side being radially inward, as shown in FIG. 2. That is, the axial length of a portion of the outer ring 3 c becomes longer as it shifts radially outward.
- the outer ring 3 c has axial end surfaces 3 f that taper off in the radially inward direction.
- the impeller 3 has a semicircular center hole 3 e , to which the motor shaft 102 is fitted to rotate the impeller 3 .
- the pump cover 4 is also made of aluminum die-cast or strong resinous material that is resistant to fuel.
- the pump passage 4 b is formed at the portion of the pump cover 4 opposite the pump passage 2 b to enclose the blades 3 a of the impeller 3 .
- the outside diameter D 1 of the impeller 3 or the outer ring 3 c is smaller than the outside diameter D 2 of the pump passage 4 b . Therefore, the outer ring 3 c , whose circumference speed is larger than other portions of the impeller 3 , is disposed within the pump passage 4 b and do not contact the surface of the pump passage 4 b or other surface of the pump cover 4 while the impeller 3 is rotating. Accordingly, the impeller 3 is not subject to wear.
- the axial end of the blades 3 a contact the surfaces of the casing 2 and the pump cover 4 opposite the blades 3 a to seal the portion between the outlet 2 c and the inlet 4 c .
- the inlet 4 c is formed in the pump cover 4 to connect the pump passages 2 b and 4 b.
- the fuel pump 100 is assembled in the following manner.
- a drive motor, a motor drive unit and the connector 103 are assembled into the housing 101 and electrically connected at first.
- the turbine pump 1 is inserted into the housing 101 .
- the pump casing 2 is force-fitted to the housing 101 , and the motor shaft 102 is fitted to the bearing 5 as shown in FIG. 1.
- the impeller 3 is inserted into the cylindrical space 2 a of the pump casing 2 , and the motor shaft 102 is inserted into the center hole 3 e .
- the pump cover 3 is positioned relative to the pump casing 2 and force-fitted into the housing 101 .
- the edge portion of the housing 101 is clamped to fix the turbine pump 1 .
- the fuel is moved radially outward again by the centrifugal force, turned by the outer ring 3 c and introduced into the pump passage 2 b .
- the fuel is repeatedly moved and circulated to increase the pressure thereof before it is discharged from the fuel outlet 2 c .
- the fuel in the pump passage 4 b is moved and circulated in the same manner as described above and shown in FIG. 2, so that two symmetrical pressuring motions of the fuel are set up in the turbine pump 1 .
- a turbine pump according to a second embodiment of the invention is described with reference to FIG. 5.
- the same reference numeral represents the same or substantially the same portion, part or components as the first embodiment hereafter.
- the outer ring 3 c is positioned so that the axial ends thereof are located within the axial ends of the impeller 3 .
- the axial end surfaces 3 f of the outer ring 3 c are not tapered off but are parallel to the axial end surfaces of the impeller.
- a turbine pump according to a third embodiment of the invention is described with reference to FIG. 6.
- the outer ring 3 c has axial end surfaces 3 f that taper off in the radially inward direction. However, the outer ring 3 c has the same axial length as the impeller 3 and is positioned so that the axial ends thereof are located to be flush the axial ends of the impeller 3 .
- a turbine pump according to a fourth embodiment of the invention is described with reference to FIG. 7.
- the outer ring 3 c and the impeller grooves 3 b are formed by a circular or cylindrical surface to be continuous so that the axial ends of the outer ring 3 c can be positioned outside the axially innermost portion 3 dl of the impeller partitions 3 d .
- the impeller grooves 3 b are alternately formed on the front and rear surfaces of the impeller in the circumferential direction. Therefore, there is no space or opening between the outer ring 3 c and the impeller partitions 3 d . Because the outer ring 3 c and the impeller partitions 3 d formed by a cylindrical surface to be continuous, the fuel can circulate more smoothly.
- the axial end of the outer ring 3 c can be tapered as the outer ring 3 c shown in FIG. 2.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
- The present application is based on and claims priority from Japanese Patent Applications 2001-97181, filed Mar. 29, 2001 and 2002-27949, filed Feb. 5, 2002, the contents of which are incorporated herein by reference.
- 1. Field of the Invention
- The present invention relates to a turbine pump that is suitable to a fuel pump to be mounted in a fuel tank of an automotive vehicle.
- 2. Description of the Related Art
- U.S. Pat. No. 5,468,119 or its corresponding publication JP-A-299983 discloses a turbine pump or peripheral pump for a fuel pump to be mounted in an automotive vehicle. The disclosed turbine pump has an outer ring at the circumference of an impeller, which is disposed in chamber walls or a pump casing. The outer ring is disposed outside the spaces (hereinafter referred to the impeller grooves) between blades of the impeller in the radial direction. The outer ring, which is disposed around the impeller grooves, has axial end surfaces flush with the axial end surfaces of the blades. The outside diameter of the impeller is larger than the outside diameter of a pump passage that is formed in the casing and the outer ring is located close to the axial end surface of the pump casing.
- In such a turbine pump, the axial distance between the impeller and the casing is arranged to be between several micrometers (μm) and tens of micrometers to prevent high-pressure fuel from leaking from the outlet side of the pump to the inlet side thereof.
- While the turbine pump is operating, the impeller moves in the axial direction due to the reaction of the pumping operation. Accordingly, the axial end surface of the outer ring of the impeller contacts the peripheral end surface of the casing.
- Because the outer ring is located at the outermost portion of the impeller, the circumferential speed is so high that the outer ring is subject to wear, which lowers pumping capacity and the lifetime thereof.
- Therefore, the present invention has been made in view of the above problems.
- It is a main object of the invention to provide a reliable turbine pump which prevents the outer ring from wearing.
- According to a main feature of the invention, an impeller of a turbine pump has a plurality of blades disposed in the circumferential direction thereof, a plurality of impeller partitions respectively disposed between every two of the blades thereby forming a plurality of impeller grooves at front and rear sides of the partitions and an outer ring disposed at the peripheral edge of the blades. Each impeller groove, each pump passage and the outer ring form a circular space for circulating fuel thereby pressuring and discharging the fuel. The outside diameter of the impeller is smaller than the outside diameter of the pump passages. Therefore, the peripheral portion of the impeller is disposed within the pump passages where the impeller does not contact any surface of the pump passages. It is more preferable that the axial ends of the outer ring are positioned within axial ends of the blades. In addition, the outer ring may have axial ends that are tapered off in the radially inward direction.
- Other objects, features and characteristics of the present invention as well as the functions of related parts of the present invention will become clear from a study of the following detailed description, the appended claims and the drawings. In the drawings:
- FIG. 1 is a partially cross-sectional side view of a turbine pump according to a first embodiment of the invention;
- FIG. 2 is a fragmentary enlarged cross-sectional side view of a portion of the turbine pump shown in FIG. 1 encircled by circle II;
- FIG. 3 is cross sectional view of a portion of the turbine pump shown in FIG. 1 cut along line III-III;
- FIG. 4 is a fragmentary enlarged perspective view of a portion of the turbine pump shown in FIG. 3 encircled by circle IV;
- FIG. 5 is a fragmentary cross-sectional view of an impeller of a turbine pump according to a second embodiment of the invention;
- FIG. 6 is a fragmentary cross-sectional view of an impeller of a turbine pump according to a third embodiment of the invention; and
- FIG. 7 is a fragmentary cross-sectional view of an impeller of a turbine pump according to a fourth embodiment of the invention.
- A turbine pump according to a first embodiment of the invention to be mounted in a fuel tank for an engine (not shown) is described with reference to FIGS.1-4.
- As shown in FIG. 1, a turbine pump1 according to a first embodiment of the invention is mounted in a
fuel pump 100 together with a drive motor (not shown), which are covered by ahousing 101. The fuel pump includes, besides the drivemotor, amotor shaft 102, anelectric connector 103, afuel chamber 104, afuel discharge pipe 105 and afuel intake pipe 4 a. When electric power is supplied to thefuel pump 100 via theconnector 103, the turbine pump 1 pumps up fuel in a fuel tank from anintake pipe 4 a and discharges the fuel from the turbine pump into thefuel chamber 104. Thereafter, the fuel is supplied to an engine via thefuel discharge pipe 105. Thefuel chamber 104 is provided inside the drive motor. - The turbine pump1 is comprised of a
pump casing 2, animpeller 3, and apump cover 4. Theimpeller 3 is rotatably disposed between thepump casing 2 and thepump cover 4. - The
pump casing 2 is made of aluminum die-cast or strong resinous material that is resistant to fuel and has acylindrical space 2 a that accommodates theimpeller 3. The axial depth ofcylindrical space 2 a is a distance between several micrometers (μm) and tens of micrometers longer than the thickness of theimpeller 3. In other words, the gap between thepump cover 4 and the impeller is the same as the gap between thepump casing 2 and theimpeller 3. As shown in FIGS. 2 and 3, apump passage 2 b is formed to be coaxial with thecylindrical space 2 a. Thepump passage 2 b is connected to theinlet 4 c at an end thereof and connected to theoutlet 2 c at the other end thereof. In the meantime, theinlet 4 c is indicated in FIG. 3 by one-dot-chain line for reference. As shown in FIG. 2, radiallyoutermost surface 2 bl of thepump passage 2 bl is included in theinner surface 2 al of thecylindrical space 2 a. In other words, the outside diameter of thepump passage 2 b is the same as the inside diameter D2 of thecylindrical space 2 a. A plurality ofblades 3 a is formed at theaxial end surface 3 g of theimpeller 3. The radial distance between the outside diameter D1 of theimpeller 3 and the inside diameter D2 of thecylindrical space 2 a is designed to be the best for pump performance. That is, the outside diameter D1 of theimpeller 3 is designed to be smaller than the outside diameter of thepump passage 2 b. Accordingly, the portion of theimpeller 3 whose circumferential speed is the maximum while the impeller rotates does not contact the surface of thepump passage 2 b or any other portion of thepump casing 2. Thepump casing 2 has abearing 5 that rotatably supports amotor shaft 102 at the center thereof. - The
impeller 3 is made of heat resistant resinous material and is disposed in thecylindrical space 2 a of thepump casing 2. As shown in FIG. 3, theimpeller 3 has a plurality ofblades 3 a formed at both the peripheral front surface that faces thepump casing 2 and the peripheral rear surface that faces thepump cover 4. Theblades 3 a formed at the front surface and the blades formed at the rear surface are disposed side by side at equal intervals in the circumferential direction. Animpeller groove 3 b is formed between each adjacent twoblades 3 a. As shown in FIG. 2,impeller partitions 3 d are disposed at an axially middle and radially inside portion thereof to protrude radially outward to divide each of theimpeller grooves 3 b into a front side groove and a rear side groove. Thus, the fuel introduced in the space (hereinafter referred to as the circular space) defined by theimpeller grooves 3 b, thepump passage 2 b of thepump casing 2 and apump passage 4 b of thepump cover 4 is circulated and pressured by theimpeller 3. Anouter ring 3 c is integrated with the plurality ofblades 3 a to connect the same at the edges thereof. In other words, theouter ring 3 c closes the circumference of theimpeller 3. The axial ends of theouter ring 3 c are positioned within the axial ends of theimpeller 3. Theouter ring 3 c has a trapezoidal cross section with the shorter side being radially inward, as shown in FIG. 2. That is, the axial length of a portion of theouter ring 3 c becomes longer as it shifts radially outward. In other words, theouter ring 3 c hasaxial end surfaces 3 f that taper off in the radially inward direction. - While the turbine pump is operating, fuel circulates in the circular spaces defined by the
impeller grooves 3 b and thepump passages outer ring 3 c is effective to smooth circulation of the fuel. - The
impeller 3 has asemicircular center hole 3 e, to which themotor shaft 102 is fitted to rotate theimpeller 3. - The
pump cover 4 is also made of aluminum die-cast or strong resinous material that is resistant to fuel. Thepump passage 4 b is formed at the portion of thepump cover 4 opposite thepump passage 2 b to enclose theblades 3 a of theimpeller 3. In other words, the outside diameter D1 of theimpeller 3 or theouter ring 3 c is smaller than the outside diameter D2 of thepump passage 4 b. Therefore, theouter ring 3 c, whose circumference speed is larger than other portions of theimpeller 3, is disposed within thepump passage 4 b and do not contact the surface of thepump passage 4 b or other surface of thepump cover 4 while theimpeller 3 is rotating. Accordingly, theimpeller 3 is not subject to wear. On the other hand, the axial end of theblades 3 a contact the surfaces of thecasing 2 and thepump cover 4 opposite theblades 3 a to seal the portion between theoutlet 2 c and theinlet 4 c. Theinlet 4 c is formed in thepump cover 4 to connect thepump passages - The
fuel pump 100 is assembled in the following manner. - A drive motor, a motor drive unit and the
connector 103 are assembled into thehousing 101 and electrically connected at first. Next, the turbine pump 1 is inserted into thehousing 101. Then, thepump casing 2 is force-fitted to thehousing 101, and themotor shaft 102 is fitted to thebearing 5 as shown in FIG. 1. Thereafter, theimpeller 3 is inserted into thecylindrical space 2 a of thepump casing 2, and themotor shaft 102 is inserted into thecenter hole 3 e. Next, thepump cover 3 is positioned relative to thepump casing 2 and force-fitted into thehousing 101. Finally, the edge portion of thehousing 101 is clamped to fix the turbine pump 1. - When the
impeller 3 is rotated by the motor in the direction indicated by an arrow in FIG. 3, fuel is pumped up from theintake pipe 4 a and introduced into the circular space via theinlet 4 c. The fuel in theimpeller grooves 3 b is circulated in the circular space defined by theimpeller grooves 3 b and thepump passages outer ring 3 c and introduced into thepump passage 2 b, as indicated by arrows in FIG. 2. The fuel is further guided by the inner surface of thepump passage 2 b, moved in the rotation direction of theimpeller 3 and introduced into theimpeller grooves 2 b. Thereafter, the fuel is moved radially outward again by the centrifugal force, turned by theouter ring 3 c and introduced into thepump passage 2 b. Thus, the fuel is repeatedly moved and circulated to increase the pressure thereof before it is discharged from thefuel outlet 2 c. The fuel in thepump passage 4 b is moved and circulated in the same manner as described above and shown in FIG. 2, so that two symmetrical pressuring motions of the fuel are set up in the turbine pump 1. - A turbine pump according to a second embodiment of the invention is described with reference to FIG. 5. In the meantime, the same reference numeral represents the same or substantially the same portion, part or components as the first embodiment hereafter.
- The
outer ring 3 c is positioned so that the axial ends thereof are located within the axial ends of theimpeller 3. However, theaxial end surfaces 3 f of theouter ring 3 c are not tapered off but are parallel to the axial end surfaces of the impeller. - A turbine pump according to a third embodiment of the invention is described with reference to FIG. 6.
- The
outer ring 3 c hasaxial end surfaces 3 f that taper off in the radially inward direction. However, theouter ring 3 c has the same axial length as theimpeller 3 and is positioned so that the axial ends thereof are located to be flush the axial ends of theimpeller 3. - A turbine pump according to a fourth embodiment of the invention is described with reference to FIG. 7.
- The
outer ring 3 c and theimpeller grooves 3 b are formed by a circular or cylindrical surface to be continuous so that the axial ends of theouter ring 3 c can be positioned outside the axiallyinnermost portion 3 dl of theimpeller partitions 3 d. Theimpeller grooves 3 b are alternately formed on the front and rear surfaces of the impeller in the circumferential direction. Therefore, there is no space or opening between theouter ring 3 c and theimpeller partitions 3 d. Because theouter ring 3 c and theimpeller partitions 3 d formed by a cylindrical surface to be continuous, the fuel can circulate more smoothly. - In this embodiment, the axial end of the
outer ring 3 c can be tapered as theouter ring 3 c shown in FIG. 2. - In the foregoing description of the present invention, the invention has been disclosed with reference to specific embodiments thereof. It will, however, be evident that various modifications and changes may be made to the specific embodiments of the present invention without departing from the scope of the invention as set forth in the appended claims. Accordingly, the description of the present invention is to be regarded in an illustrative, rather than a restrictive, sense.
Claims (8)
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001-97181 | 2001-03-29 | ||
JP2001-097181 | 2001-03-29 | ||
JP2001097181 | 2001-03-29 | ||
JP2002-27949 | 2002-02-05 | ||
JP2002-027949 | 2002-02-05 | ||
JP2002027949A JP2002357191A (en) | 2001-03-29 | 2002-02-05 | Turbine pump |
Publications (2)
Publication Number | Publication Date |
---|---|
US20020141860A1 true US20020141860A1 (en) | 2002-10-03 |
US6729841B2 US6729841B2 (en) | 2004-05-04 |
Family
ID=26612626
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/107,209 Expired - Lifetime US6729841B2 (en) | 2001-03-29 | 2002-03-28 | Turbine pump |
Country Status (2)
Country | Link |
---|---|
US (1) | US6729841B2 (en) |
JP (1) | JP2002357191A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20030086783A1 (en) * | 2001-11-06 | 2003-05-08 | Atsushige Kobayashi | Fuel pump having an impeller |
US7037066B2 (en) | 2002-06-18 | 2006-05-02 | Ti Group Automotive Systems, L.L.C. | Turbine fuel pump impeller |
US9249806B2 (en) | 2011-02-04 | 2016-02-02 | Ti Group Automotive Systems, L.L.C. | Impeller and fluid pump |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5017086A (en) * | 1989-05-08 | 1991-05-21 | Vickers Incorporated | Hydraulic periphery pumps |
US5310308A (en) * | 1993-10-04 | 1994-05-10 | Ford Motor Company | Automotive fuel pump housing with rotary pumping element |
US5702229A (en) * | 1996-10-08 | 1997-12-30 | Walbro Corporation | Regenerative fuel pump |
US5961276A (en) * | 1997-05-09 | 1999-10-05 | Robert Bosch Gmbh | Aggregate for feeding a fuel from tank to an internal combustion engine of a motor vehicle |
US6174128B1 (en) * | 1999-02-08 | 2001-01-16 | Ford Global Technologies, Inc. | Impeller for electric automotive fuel pump |
US6464450B1 (en) * | 2000-09-06 | 2002-10-15 | Delphi Technologies, Inc. | Fuel pump |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4307353A1 (en) | 1993-03-09 | 1994-09-15 | Bosch Gmbh Robert | Peripheral pump, especially for delivering fuel from a storage tank to the internal combustion engine of a motor vehicle |
JPH08277793A (en) | 1995-04-05 | 1996-10-22 | Nippondenso Co Ltd | Fuel pump |
JPH0979168A (en) | 1995-09-12 | 1997-03-25 | Unisia Jecs Corp | Turbine pump |
JPH0979170A (en) | 1995-09-12 | 1997-03-25 | Unisia Jecs Corp | Turbine pump |
-
2002
- 2002-02-05 JP JP2002027949A patent/JP2002357191A/en active Pending
- 2002-03-28 US US10/107,209 patent/US6729841B2/en not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5017086A (en) * | 1989-05-08 | 1991-05-21 | Vickers Incorporated | Hydraulic periphery pumps |
US5310308A (en) * | 1993-10-04 | 1994-05-10 | Ford Motor Company | Automotive fuel pump housing with rotary pumping element |
US5702229A (en) * | 1996-10-08 | 1997-12-30 | Walbro Corporation | Regenerative fuel pump |
US5961276A (en) * | 1997-05-09 | 1999-10-05 | Robert Bosch Gmbh | Aggregate for feeding a fuel from tank to an internal combustion engine of a motor vehicle |
US6174128B1 (en) * | 1999-02-08 | 2001-01-16 | Ford Global Technologies, Inc. | Impeller for electric automotive fuel pump |
US6464450B1 (en) * | 2000-09-06 | 2002-10-15 | Delphi Technologies, Inc. | Fuel pump |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20030086783A1 (en) * | 2001-11-06 | 2003-05-08 | Atsushige Kobayashi | Fuel pump having an impeller |
US7037066B2 (en) | 2002-06-18 | 2006-05-02 | Ti Group Automotive Systems, L.L.C. | Turbine fuel pump impeller |
US9249806B2 (en) | 2011-02-04 | 2016-02-02 | Ti Group Automotive Systems, L.L.C. | Impeller and fluid pump |
Also Published As
Publication number | Publication date |
---|---|
US6729841B2 (en) | 2004-05-04 |
JP2002357191A (en) | 2002-12-13 |
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